WO2015000629A1 - Rotor pour dispositif turbocompresseur, dispositif turbocompresseur équipé d'un rotor et arbre pour un tel rotor - Google Patents

Rotor pour dispositif turbocompresseur, dispositif turbocompresseur équipé d'un rotor et arbre pour un tel rotor Download PDF

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Publication number
WO2015000629A1
WO2015000629A1 PCT/EP2014/060290 EP2014060290W WO2015000629A1 WO 2015000629 A1 WO2015000629 A1 WO 2015000629A1 EP 2014060290 W EP2014060290 W EP 2014060290W WO 2015000629 A1 WO2015000629 A1 WO 2015000629A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
external thread
rotor
bearing element
thread
Prior art date
Application number
PCT/EP2014/060290
Other languages
German (de)
English (en)
Inventor
Ralf Böning
Ralph-Maurice KÖMPEL
Original Assignee
Continental Automotive Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Automotive Gmbh filed Critical Continental Automotive Gmbh
Priority to EP14727172.0A priority Critical patent/EP3017146B1/fr
Priority to US14/902,521 priority patent/US10227992B2/en
Priority to CN201480037586.7A priority patent/CN105339589B/zh
Publication of WO2015000629A1 publication Critical patent/WO2015000629A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/025—Fixing blade carrying members on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

Definitions

  • the invention is in the field of mechanics, especially of mechanical engineering and can be used with particular advantage in turbocharging ⁇ devices.
  • internal combustion engines in the form of piston engines are used for internal combustion engines in the form of piston engines.
  • Turbocharger devices are used to assist the air intake of the pistons by providing an overpressure of the incoming air.
  • a turbocharger usually has a turbine which is driven in the exhaust gas flow by hot air and which is fixedly mounted on a common shaft with a compressor wheel, which in turn causes an increase in pressure of the inflowing air in the supply air duct of the internal combustion engine.
  • the shaft that connects the turbine to the compressor wheel requires considerable torque to be transmitted at very high speeds (several 10,000 - 100,000 revolutions per minute).
  • Challenges in mechanical design include stability against high temperatures in the exhaust stream and shaft bearing for very high speeds.
  • there are also additional problems in the design of the oil lubrication of the bearings which are usually designed as plain bearings, partly with floating bushings.
  • On the shaft bearing elements for the radial ⁇ storage and the axial bearing and sealing elements for the sealing of the oil space in the housing of the turbo charger device are accordingly reliable and stable to arrange.
  • a known construction in this context builds on a axial bearing element, a sealing sleeve member and a compressor wheel (impeller) axially successively postpone by a first end of the shaft and then by means of a central threaded nut which is screwed onto an external thread of the shaft, in the axial direction so close to each other tension, that no loosening of the individual parts against the shaft is to be feared even with the mechanical loads during operation and these rotate with the shaft.
  • An additional measure to ensure the cohesion of said arrangements may be that a certain elasticity and / or an elastic element is provided to compensate for a possible setting behavior of the parts.
  • the shaft shaft could be designed as an "expansion screw".
  • the present invention is based on the background of the prior art the object to provide a rotor for a turbocharger device, in which a permanent and reliable cohesion of the individual parts is ensured in a technically simple and cost-effective manner.
  • the invention relates specifically to a rotor for a turbocharger device including a shaft as well as with a paddle wheel, a sealing bush element and a rotating with the shaft thrust bearing, the axially back on the shaft behind the other arranged and fixed, wherein the log ⁇ tung sleeve member and the rotating Axial bearing element are screwed by means of an at least one of these elements provided internal thread with a shaft arranged on the first outer thread and braced against a shaft shoulder.
  • a threaded bushing associated with the sealing sleeve element and / or with the axial bearing element rotating with the shaft with the shaft at least one of these parts is firmly connected to the shaft and fixed and optionally clamped the other part between the bolted part and a shaft shoulder.
  • the paddle wheel which typically can be designed as a compressor wheel, can additionally be fixed by its own fixation, for example a further screw connection on the shaft at its first end. It is possible in this way to fix the individual parts on the shaft stronger and more reliable and to ensure the cohesion of the remaining parts even when solving a single part.
  • the elastic forces that can be generated are greater than in the fixation of all items by means of a single screw on the shaft end.
  • the log ⁇ tung sleeve member has an internal thread, which is screwed with a first external thread of the shaft and that the rotating with the shaft thrust bearing is disposed axially between the seal cup member and the shaft shoulder.
  • the axial bearing element which for example essentially has an annular axial bearing disk, can be freely displaceable on the shaft.
  • the thrust bearing element is in this case exclusively by the fit on the shaft in the radial direction and by the clamping action of the
  • the axial bearing element has an internal thread which is screwed to an external thread of the shaft.
  • the thrust bearing element is additionally bolted to an external thread of the shaft and pressed against a Wel ⁇ lenschulter. In this way, the axial pressing pressure can be added by the individual screw connections of the sealing bush element and the axial bearing element.
  • the Axialla- gerelement or an axial portion of the thrust bearing element is integrally formed with the sealing bushing element.
  • the number of slid on the shaft items can be reduced and their cohesion can be further improved.
  • the transmittable by the rotor torque is increased and increases the stiffness of the rotor as a whole.
  • the additionally transmissible torque is then determined by the friction between the impeller and the seal bushing element on the one hand and the friction between the thrust bearing element and the shaft shoulder on the other hand.
  • Turbocharger in operation and also in the expected changes in rotational speeds corresponding to different load conditions of the engine is very beneficial.
  • the release of individual parts of the rotor by vibrations is also less likely in this way.
  • a further advantageous embodiment of the invention provides that the paddle wheel is braced axially by means of a screwed centrally from the end of the shaft ago central Verschraubungselements, in particular a screwed onto a second external thread of the shaft nut relative to the gasket sleeve element, the thrust bearing element and in particular the shaft shoulder.
  • the axial compression of the pushed parts increases the stiffness of the rotor beyond the rigidity of the shaft body. It is also conceivable, in a blind bore of the shaft to introduce an internal thread into which a closure body can be screwed, which extends outwardly beyond the diameter of the shaft out there, the shaft there is usually a one-sided screw engages and applies an axial force on the paddle wheel.
  • the invention can also be advantageously configured in that the second external thread of the shaft and the first external thread of the shaft have opposing slopes.
  • a torque applied to the paddle wheel which may for example in operation consist in the air resistance which is opposed to a rotation of the paddle wheel, rotates the paddle wheel with respect to the shaft, and is also prevented from being adjacent to the paddle wheel Element, so typically the seal bushing element is rotated by the static friction forces in the same direction.
  • the second external thread of the shaft and the first external thread of the shaft in the same direction inclines with different pitch angles, wherein the first external thread is formed steeper than the second external thread.
  • the external thread is also when one of the parts is rotated, co-rotation of the static friction partner, so for example in primary rotation of the impeller, the co-rotation of the Dichtungsbuchselements prevented since the different pitches of the thread would cause an amplification of the pressing together of the parts, which is prevented by the already produced from the beginning during assembly pressing pressure.
  • the invention relates not only to a rotor, as has already been described above, on a turbocharger device with such a rotor and with a housing, wherein on the housing according to the invention, a housing fixed axial bearing disc is arranged, the ring-segment-shaped, to one side open for assembly and interspersed by the shaft.
  • the shaft usually preassembled as a whole, that is also connected to the deferred parts, such as rotating with the shaft thrust bearing element, a sealing sleeve member and an impeller, is connected to the housing, the rotor is usually from one side transverse to the longitudinal direction of the shaft in to insert the housing.
  • the shaft is not hin beschiebbar by annular housing-fixed bearing elements and must either be pre-assembled with all annular bearing elements or inserted into the housing-fixed bearing elements from the side.
  • This is made possible with respect to an axial bearing disc ⁇ the fact that the housing-Axialla ⁇ gerusion no complete ring but only a ring segment with an opening into which the shaft can be inserted with the rotating with the shaft thrust bearing element.
  • Another part of the housing-fixed thrust washer can be added and screwed after assembly of the shaft to complete the thrust bearing.
  • the present invention also relates to a shaft for a rotor of the type described above, wherein the shaft between a first shaft end and a
  • Shaft shoulder on which the shaft, seen from the first shaft end, increases its diameter abruptly, has a first external thread, and that the shaft in addition to the first external thread another thread, in particular a second external thread, which is spatially separated from the first external thread is.
  • FIG. 1 shows a longitudinal section through a rotor of a turbocharger device according to the prior art with a part of a housing
  • 2 is a partial enlargement of FIG. 1
  • FIG. 3 shows a longitudinal section of a rotor of a turbocharger device according to the invention with a part of a housing
  • FIG. 4 is an enlarged detail of FIG. 3,
  • FIGS. FIGS. 5 to 8 show various views of a combination bushing which combines a seal bushing element and a thrust bearing element rotating with the shaft,
  • FIG. 9 is an illustration of a rotor partially in a side view, partially in longitudinal section with a compressor wheel and a pushed onto the shaft combination socket,
  • FIG. 10 shows the illustration from FIG. 9, with the compressor wheel and the combination bush being omitted, FIG.
  • Fig. 13 is a detail view of a shaft with these parts pushed onto the parts of the rotating with the shaft thrust bearing element and a screwed
  • FIG. 15 is a side view of a matching with the parts shown in Fig. 14 runner with a partially unexposed shaft
  • FIG. 16 shows a rotor which is equipped with the parts shown in FIG. 14 and a compressor wheel
  • FIG. Fig. 17 is a detail of a combination socket on a shaft in longitudinal section and
  • Fig. 18 shows a further detail view of another exemplary form of a combination socket on a shaft in longitudinal section ⁇ .
  • FIG. 1 shows a part of a turbocharger device 2 according to the prior art in a longitudinal section through the shaft of the rotor and a partial view of housing parts.
  • the rotor has on the exhaust side a turbine wheel 18, which is driven by the exhaust gas flow of a combustion piston engine.
  • the turbine wheel 18 is mounted on a common shaft 3 with a paddle wheel / compressor wheel 4 which delivers air in an air intake passage to the intake valves of the internal combustion engine and compresses with the aim of more effective combustion in the piston chambers.
  • the compressor wheel 4 is fastened to the shaft 3 by means of a threaded nut 13, which is screwed as a centric screwing element on an end-side external thread of the shaft 3 and compresses the compressor wheel 4 with the interposition of various additional elements against a shaft shoulder.
  • a threaded nut 13 which is screwed as a centric screwing element on an end-side external thread of the shaft 3 and compresses the compressor wheel 4 with the interposition of various additional elements against a shaft shoulder.
  • two radial bearings 19, 20 are also provided, which also serve for the radial storage of the shaft 3 at the typically several tens of thousands of revolutions per minute to a few hundred thousand revolutions per minute amounts.
  • the radial bearings are designed, for example, as floating plain bearings, in which the floating bushings can rotate relative to housing-fixed bearing elements with about half the number of revolutions of the shaft.
  • FIG. 2 shows a detail of FIG. 1, enlarged in detail, wherein in particular except the compressor 4, the jammed between this and a shaft shoulder 12 annular components are shown, of which a first one sealing bushing element 5, a second a first part 8 is a rotating shaft with the axial bearing and a third a second part 8 'of a rotating with the shaft thrust bearing ⁇ elements.
  • the three mentioned clamped elements 5, 8, 8 ' are freely displaceable in the axial direction on the shaft 3 and are held exclusively by static friction forces between the compressor wheel 4 and the shaft shoulder 12.
  • the housing-fixed Axi ⁇ allagerarea 9 thus forms a substantially annular or annular sector-shaped disc on which the two parts 8, 8 'of the rotating with the shaft thrust bearing element and slide are guided.
  • Fig. 3 shows in the context of the invention, a construction in which on a shaft 3 ', which carries a first external thread 11, a combination socket 22 is screwed, which is a sealing bushing element and a first and a second part of a rotating with the shaft Axiallagerelements integrally united in itself. It is only the axial portion corresponding to the log ⁇ tung sleeve member ver ⁇ see with an internal thread which is screwed onto the corresponding first external thread 11 of the shaft. The first and second part of the thrust bearing ⁇ elements are not provided with an internal thread and pushed onto the first external thread 11 adjacent axial portion of the shaft in a precise fit.
  • the combination bush 22 is firmly clamped against a shaft shoulder 12 of the shaft 3 'by the screw. From the first end 23 of the shaft 3 'ago also a compressor 4 is pushed onto the shaft 3' and by means of a threaded nut 13 with respect to the Combined socket 22 pressed. The threaded nut 13 is screwed onto a second external thread 14 at the first end 23 of the shaft 3 '.
  • the threaded nut 13 has for this purpose a matching outer contour, for example, a hexagonal contour on.
  • the combination bush 22 may have on at least one of its elements, that is, for example, at the axial portion of the seal bushing element, but advantageously on one of the parts that correspond to the rotating with the shaft thrust bearing element, an octagonal or square contour, the attack of a tool, for example a screw ⁇ wrench allows to screw.
  • FIG. 4 shows the construction shown in an oversized manner in FIG. 3 in a section in greater detail. It is the combination socket 22 shown enlarged with a first axial portion 5 corresponding to a Dichtungsbuchsenelement, a second portion corresponding to the first part 8 of a rotating thrust bearing element and a third portion which corresponds to the second part 8 ⁇ of a rotating shaft with the Axiallagerelements ,
  • the individual sections are delimited in FIG. 4 by dashed lines against each other. It is also apparent from Fig.
  • the second and third axial portion of the combination bushing 22, formed by the first part 8 and the second part 8 'of the thrust bearing element are not provided with an internal thread but with a cylindrical inner surface 24, over the first external thread 11 of the shaft 3 'is axially pushed over.
  • the first external thread 11 is over-turned, ie machined such that the outer contour of the external thread 11 corresponds as exactly as possible to the outer contour of the well 3 'in the area of the cylindrical inner surface 24 of the elements 8, 8'.
  • FIGS. 5, 6, 7 and 8 show, from different views, the combination bushing 22, in FIG. 5 in one
  • FIG. 7 Front view, in a side view in FIG. 6, in a longitudinal section in FIG. 7 and in a three-dimensional view in FIG. 8.
  • the axial sections of the combination bushing 22 can be seen corresponding to the sealing bushing element 5, the first part 8 of the axial bearing element and the second part 8 ⁇ of the axial bearing element.
  • the sealing bushing element 5 has an internal thread 10.
  • FIG. 9 shows a side view and partially longitudinally sectioned view of a rotor 1, as it is basically already shown in FIGS. 3 and 4 can be seen. It can be seen particularly clearly from FIG. 9 that the contact surface 26 on which the compressor wheel 4 rests against the combiner bushing 22 is larger than the contact surface which the combination bush 22 has in the contact region 27 with the shaft shoulder 12. It will be clear that a considerable torque can thus be transmitted in the region between the combination bush 22 and the compressor wheel 4. This is particularly advantageous when the transferred
  • Fig. 10 shows the runner in FIG. 9 without the Deferred combination socket, the compressor wheel and the mounting ⁇ nut 13, but with the first male thread 11, which is significantly spaced axially from the second external thread 14.
  • FIG. 11 shows, in a three-dimensional view, a housing-fixed axial bearing disk 9 which has a ring-segment-shaped bearing surface 9 '. This is interrupted in an angular range of about 60 ° in order to keep open to this side of the housing fixed thrust washer and to allow lateral insertion of the shaft and the rotating shaft with the thrust bearing element.
  • the first and second part 8 ' are positioned 8' of the rotating with the shaft thrust bearing ⁇ elements on both sides of the housing-fixed axial bearing.
  • each one of the elements 5, 8, 8 ⁇ can be constructed in this way an axial pressure, so that the individual parts are very well secured against loosening
  • each of the B Parts 5, 8, 8 ⁇ provided with a peripheral outer contour, which allows the attack of a tool, such as a ringen sayis to tighten each of the elements individually on the thread 11 can.
  • the thread 11 extends almost to the shaft shoulder 12, wherein there is still an axial distance between the end of the external thread 11 and the shaft shoulder 12 is seen.
  • the shaft 3 ''' has at least three axial From ⁇ sections with different diameters, wherein the portion forms with the largest diameter, the shaft shoulder 12, an area with a smaller external diameter, the external thread 11 transmits and relative to the provided with the external thread 11 axial portion of the Shaft a the first shaft end 23 facing axial region is further reduced in diameter, so that the elements 5, 8, 8 ⁇ on the shaft via the first shaft end 23 can be pushed up to the external thread 11 point.
  • this has the second external thread 14 for screwing on a threaded nut and for fastening a compressor wheel between the threaded nut 13 and the sealing sleeve element 5.
  • FIG. 16 shows the assembled rotor in a partially longitudinal sectioned image
  • the Fign. 17 and 18 each show a construction in which the first part 8 of the axial bearing element rotating with the shaft is integrally combined with the sealing bushing element 5.
  • the so-called bearing collar that is to say the second part 8 ⁇ of the axial bearing element, is separated from the first part 8 of the axial bearing element and formed as an independent body.
  • the housing-fixed thrust washer can be formed as a two-part fully annular bearing element.
  • the combined into one piece combination socket which combines the parts 5 (sealing sleeve member) and 8 (first part of the thrust bearing element) in itself, can be screwed separately on the external thread 11 'of the shaft.
  • the described embodiments of the invention allow a particularly strong cohesion of the various pushed onto a shaft parts, such as the parts of the rotating shaft with the thrust bearing element, a sealing bush and a compressor wheel.
  • the flexural rigidity of the rotor is increased by a particularly firm connection of the applied to the shaft parts and thus reduces the susceptibility to vibration of the shaft and the susceptibility to the formation of imbalances.
  • particularly large torques between a turbine wheel and a Ver ⁇ dichterrad can be transmitted by the arrangements described.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un rotor (1) qui est destiné à un dispositif turbocompresseur (2) et qui est équipé d'un arbre (3, 3', 3'') ainsi que d'une roue à aubes (4), d'un manchon d'étanchéité (5) et d'un élément de butée axiale (8, 8'), tournant conjointement avec l'arbre, lesquels sont disposés et fixés axialement les uns derrière les autres sur l'arbre (3, 3', 3''). La douille d'étanchéité (5) et l'élément de butée axiale (8, 8') sont vissés au moyen d'un filetage intérieur (10, 10', 10'') formé sur au moins un de ces éléments, à un premier filetage extérieur (11, 11') formé sur l'arbre (3, 3', 3'') et sont calés contre un épaulement (12) de l'arbre. Cette construction permet de fixer plus solidement et avec une plus grande rigidité les pièces enfilées sur l'arbre et donc d'obtenir une plus faible sensibilité aux vibrations pendant le fonctionnement.
PCT/EP2014/060290 2013-07-03 2014-05-20 Rotor pour dispositif turbocompresseur, dispositif turbocompresseur équipé d'un rotor et arbre pour un tel rotor WO2015000629A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP14727172.0A EP3017146B1 (fr) 2013-07-03 2014-05-20 Rotor pour dispositif turbocompresseur, dispositif turbocompresseur équipé d'un rotor et arbre pour un tel rotor
US14/902,521 US10227992B2 (en) 2013-07-03 2014-05-20 Rotor for a turbocharger device, turbocharger device having a rotor, and shaft for a rotor of said type
CN201480037586.7A CN105339589B (zh) 2013-07-03 2014-05-20 用于涡轮增压器装置的转子、具有转子的涡轮增压器装置和用于这种转子的轴

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013213023.6 2013-07-03
DE102013213023.6A DE102013213023A1 (de) 2013-07-03 2013-07-03 Läufer für eine Turboladereinrichtung, Turboladereinrichtung mit einem Läufer und Welle für einen solchen Läufer

Publications (1)

Publication Number Publication Date
WO2015000629A1 true WO2015000629A1 (fr) 2015-01-08

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Application Number Title Priority Date Filing Date
PCT/EP2014/060290 WO2015000629A1 (fr) 2013-07-03 2014-05-20 Rotor pour dispositif turbocompresseur, dispositif turbocompresseur équipé d'un rotor et arbre pour un tel rotor

Country Status (5)

Country Link
US (1) US10227992B2 (fr)
EP (1) EP3017146B1 (fr)
CN (1) CN105339589B (fr)
DE (1) DE102013213023A1 (fr)
WO (1) WO2015000629A1 (fr)

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DE102016207698A1 (de) * 2016-05-04 2017-11-09 Bosch Mahle Turbo Systems Gmbh & Co. Kg Ladeeinrichtung
FR3077105B1 (fr) * 2018-01-19 2020-02-14 Safran Electrical & Power Ventilateur pour un groupe de refroidissement d'aeronef
CN108804794B (zh) * 2018-05-31 2019-03-05 北京航空航天大学 一种基于分区的涡轮盘疲劳寿命及失效风险评估方法
KR101989588B1 (ko) * 2018-11-27 2019-06-14 터보윈 주식회사 서지 영역에서의 운전이 가능한 터보 블로어
CN114837748A (zh) * 2021-02-02 2022-08-02 中国航发商用航空发动机有限责任公司 航空发动机
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DE102013213023A1 (de) 2015-01-08
EP3017146A1 (fr) 2016-05-11
US10227992B2 (en) 2019-03-12
CN105339589A (zh) 2016-02-17
CN105339589B (zh) 2017-09-15
EP3017146B1 (fr) 2017-07-19
US20160377089A1 (en) 2016-12-29

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